CN202006219U - Hydraulic control system - Google Patents

Hydraulic control system Download PDF

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Publication number
CN202006219U
CN202006219U CN201120014866XU CN201120014866U CN202006219U CN 202006219 U CN202006219 U CN 202006219U CN 201120014866X U CN201120014866X U CN 201120014866XU CN 201120014866 U CN201120014866 U CN 201120014866U CN 202006219 U CN202006219 U CN 202006219U
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valve
oil cylinder
pressure
pressure switch
mouth
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CN201120014866XU
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Chinese (zh)
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玉瑞智
张元�
高红玉
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Beris Engineering and Research Corp
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Beris Engineering and Research Corp
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Abstract

The utility model discloses a hydraulic control system which is used for controlling a casting and rolling machine for a continuous casting and rolling line of free thickness slabs. The hydraulic control system comprises a first roller-depressing oil-cylinder control system, a second roller-depressing oil-cylinder control system, an upper connecting shaft holding hydraulic cylinder control system, a lower connecting shaft holding hydraulic cylinder control system, an upper roller axial locking control system, a lower roller axial locking control system, a first side temper mill locking hydraulic cylinder control system, a second side temper mill locking hydraulic cylinder control system, a track lifting cylinder control system, a roller-changing cylinder control system, a top roller balance cylinder control system, an upper connecting shaft balance cylinder control system and a lower connecting shaft balance cylinder control system. The hydraulic control system can improve the efficiency and the quality of products.

Description

Hydraulic control system
Technical field
The utility model relates to metallurgy industry continuous casting equipment field, relates in particular to the hydraulic control system of a kind of casting and rolling machine and swing fan-shaped section.
Background technology
Sheet billet continuous casting is important step in the high-quality Wide and Thick Slab production procedure, and the main online equipment in the conventional slab caster type comprises: big Bao Tai, middle hired car, crystallizer and vibrating device, fan-shaped section etc.In addition, a cover casting and rolling machine and two cover swing fan-shaped section have been added on the basis of the capital equipment of special continuous casting main online equipment in above-mentioned conventional slab caster type.When cooperating casting-rolling technology to realize, the research and development of the hydraulic pressure of the hydraulic control of swing fan-shaped section and casting and rolling machine being depressed control are imperative.
Existing milling train auxiliary hydraulic system, its upper joint-shaft is held hydraulic cylinder control system tightly, bottom spindle is held hydraulic cylinder control system, topping roll axial locking control system, bottom roll axial locking control system, side planisher locking hydraulic cylinder control system tightly by two four-way electromagnetic reversing valves, a superposing type Double throttle check valve composition, do not have pressure switch to detect the pressure of relevant oil circuit, in case and system's leakage of oil liquid can't cut off relevant oil circuit; And its roll change cylinder control system only is made up of an electro-hydraulic reversing valve, a superposing type Double throttle check valve and four travel switches, this system's control accuracy is low, during motion compression shock big, be not easy to operation.
In sum, the casting and rolling machine auxiliary hydraulic system of prior art can not satisfy the requirement of free thickness slab continuous casting and rolling line as can be known, therefore is necessary to propose improved technological means, solves this problem.
The utility model content
For addressing the above problem, the utility model provides a kind of hydraulic control system, be used to control the casting and rolling machine of free thickness slab continuous casting and rolling line, this hydraulic control system comprises: the first roll depress oil cylinder control system, the second roll depress oil cylinder control system, upper joint-shaft is held hydraulic cylinder control system tightly, bottom spindle is held hydraulic cylinder control system tightly, topping roll axial locking control system, bottom roll axial locking control system, first side planisher locking hydraulic cylinder control system, second side planisher locking hydraulic cylinder control system, track lift cylinders control system, roll change cylinder control system, top roll compensating cylinder control system, upper joint-shaft compensating cylinder control system, bottom spindle compensating cylinder control system.
Compared with prior art, according to technique scheme of the present utility model, this hydraulic control system is sturdy and durable, steadily reliable, can realize good control to casting bundle machine, has improved product efficiency and quality, has reached the requirement of the production technology of casting and rolling machine.
Description of drawings
Accompanying drawing described herein is used to provide further understanding of the present utility model, constitutes the application's a part, and illustrative examples of the present utility model and explanation thereof are used to explain the utility model, do not constitute improper qualification of the present utility model.In the accompanying drawings:
Fig. 1 and Fig. 2 are the roll depress oil cylinder control system schematic diagram of casting and rolling machine of the present utility model;
Fig. 3 A to Fig. 3 H is a schematic diagram of the auxiliary hydraulic pressure control system of casting and rolling machine of the present utility model;
Fig. 4 A to Fig. 4 C is another schematic diagram of the auxiliary hydraulic pressure control system of casting and rolling machine of the present utility model;
Fig. 5 is the hydraulic control system schematic diagram of the utility model swing fan-shaped section.
The specific embodiment
For making the purpose of this utility model, technical scheme and advantage clearer,, the utility model is described in further detail below in conjunction with drawings and the specific embodiments.
Hydraulic control system according to embodiment of the present utility model comprises: two cover rolls are depressed oily cylinder control system, one cover top roll compensating cylinder control system, one puts and connects spindle balance cylinder control system, one cover bottom spindle compensating cylinder control system, one cover upper joint-shaft is held hydraulic cylinder control system tightly, one cover bottom spindle is held hydraulic cylinder control system tightly, one puts roll axial locking control system, one cover bottom roll axial locking control system, two cover side planisher locking hydraulic cylinder control systems, an one cover track lift cylinders control system and a cover roll change cylinder control system.
Two cover rolls are depressed oily cylinder control system realization to the roll gap adjusting of the roll of casting and rolling machine and the control of roll-force.Top roll compensating cylinder control system realizes topping roll is carried out balance, and the roll that makes the topping roll of casting and rolling machine to follow is fast depressed oil cylinder and moved up and down.Upper joint-shaft compensating cylinder control system realizes that the last direction to casting and rolling machine connects and spool carries out balance.Bottom spindle compensating cylinder control system realizes that the following direction to casting and rolling machine connects axle and carries out balance.The hydraulic cylinder control system of upper joint-shaft holding tightly realizes the upper joint-shaft of casting and rolling machine is locked.The hydraulic cylinder control system of bottom spindle holding tightly realizes the bottom spindle of casting and rolling machine is locked.Topping roll axial locking control system realizes the topping roll of casting and rolling machine is carried out axial locking.Bottom roll axial locking control system realizes the bottom roll of casting and rolling machine is carried out axial locking.Side planisher locking hydraulic cylinder control system realizes the side planisher of casting and rolling machine is locked.Track lift cylinders control system realizes the roll change track of casting and rolling machine is carried out lifting control.Roll change cylinder control system can be controlled the speed of roll change cylinder, realizes the control of roll change process medium velocity.
Fig. 1 and Fig. 2 are the roll depress oil cylinder control system schematic diagram of casting and rolling machine of the present utility model.This roll depress oil cylinder control system is made up of first roll depress oil cylinder control system (being transmission side HGC (Hydraulic Gauge Control) cylinder hydraulic control system) and the second roll depress oil cylinder control system (being fore side HGC oil cylinder hydraulic control system).The first roll depress oil cylinder control system is used to control the transmission side HGC oil cylinder of casting and rolling machine, and the second roll depress oil cylinder control system is used to control the fore side HGC oil cylinder of casting and rolling machine.This first roll depress oil cylinder control system and the second roll depress oil cylinder control system are the diaxon synchronous control system.
With reference to figure 1 and Fig. 2, the first roll depress oil cylinder control system mainly comprises: first servo valve 111.1, second servo valve 111.2, first solenoid directional control valve 112, first hydraulic control one-way valve 113.1, second hydraulic control one-way valve 113.2, the 3rd hydraulic control one-way valve 113.3, the 4th hydraulic control one-way valve 113.4, first high pressure filter 114, first electromagnetic relief valve 115, first pressure-reducing valve 116, first servo-cylinder 117, first pressure sensor 118.1, second pressure sensor 118.2, first displacement transducer 119, the first low pressure accumulator group 120, the first high pressure accumulator group 121.Wherein, the oil-in A of first high pressure filter 114 links to each other with oil sources hydraulic oil P pipe, the oil-out B of first high pressure filter 114 links to each other with guide's hydraulic fluid port X of first servo valve 111.1 and guide's hydraulic fluid port X of second servo valve 111.2 respectively, for the pilot valve of the pilot valve of first servo valve 111.1 and second servo valve 111.2 provides high-precision control oil.The P mouth of first servo valve 111.1 links to each other with the A mouth of first hydraulic control one-way valve 113.1, and the T mouth links to each other with the oil return pipe T pipe of hydraulic oil source, and the A mouth links to each other with the A mouth of the 3rd hydraulic control one-way valve 113.3.The P mouth of second servo valve 111.2 links to each other with the A mouth of second hydraulic control one-way valve 113.2, and the T mouth links to each other with the oil return pipe T pipe of hydraulic oil source, and the A mouth links to each other with the A mouth of the 4th hydraulic control one-way valve 113.4.The P mouth of first solenoid directional control valve 112 links to each other with oil sources hydraulic oil P pipe, and the B mouth links to each other with the X mouth of second hydraulic control one-way valve 113.2, the X mouth of the 4th hydraulic control one-way valve 113.4, the X mouth of the 6th hydraulic control one-way valve 213.2 and the X mouth of the 8th hydraulic control one-way valve 213.4 respectively.The A1 mouth of first hydraulic control one-way valve 113.1 links to each other with oil sources hydraulic oil P pipe, and the A mouth links to each other with the P mouth of first servo valve 111.1.The A1 mouth of second hydraulic control one-way valve 113.2 links to each other with oil sources hydraulic oil P pipe, and the A mouth links to each other with the P mouth of second servo valve 111.2.The A1 mouth of the 3rd hydraulic control one-way valve 113.3 links to each other with the rodless cavity A mouth of first servo-cylinder 117, and the A mouth links to each other with the A mouth of first servo valve 111.1.The A1 mouth of the 4th hydraulic control one-way valve 113.4 links to each other with the rodless cavity A mouth of first servo-cylinder 117, and the A mouth links to each other with the A mouth of second servo valve 111.2.The A mouth of first electromagnetic relief valve 115 links to each other with the rodless cavity A mouth of first servo-cylinder 117, and the B mouth links to each other with the oil return pipe T pipe of hydraulic oil source.The A mouth of first pressure-reducing valve 116 links to each other with the rod chamber B mouth of first servo-cylinder 117, and the B mouth links to each other with oil sources hydraulic oil P pipe, the T mouth links to each other with the oil return pipe T pipe of hydraulic oil source.The pressure tap of first pressure sensor 118.1 links to each other with the rodless cavity A mouth of first servo-cylinder 117.The pressure tap of second pressure sensor 118.2 links to each other with the rod chamber B mouth of first servo-cylinder 117.First displacement transducer 119.1 is installed on the transmission side HGC cylinder.The PS mouth of the first low pressure accumulator group 120 links to each other with the rod chamber B mouth of first servo-cylinder 117, and the T mouth links to each other with the oil return pipe T pipe of hydraulic oil source.The P3 mouth of the first high pressure accumulator group 121 links to each other with the A1 mouth of first hydraulic control one-way valve 113.1 and the A1 mouth of second hydraulic control one-way valve 113.2 respectively.
With reference to figure 1 and Fig. 2, the first roll depress oil cylinder control system mainly comprises: the 3rd servo valve 211.1, the 4th servo valve 211.2, second solenoid directional control valve 212, the 5th hydraulic control one-way valve 213.1, the 6th hydraulic control one-way valve 213.2, the 7th hydraulic control one-way valve 213.3, the 8th hydraulic control one-way valve 213.4, second high pressure filter 214, second electromagnetic relief valve 215, second pressure-reducing valve 216, second servo-cylinder 217, the 3rd pressure sensor 218.1, the 4th pressure sensor 218.2, second displacement transducer 219, the second low pressure accumulator group 220, the second high pressure accumulator group 221.Wherein, the oil-in A of second high pressure filter 214 links to each other with oil sources hydraulic oil P pipe, the oil-out B of second high pressure filter 214 links to each other with guide's hydraulic fluid port X of the 3rd servo valve 211.1 and guide's hydraulic fluid port X of the 4th servo valve 211.2 respectively, for the pilot valve of the pilot valve of the 3rd servo valve 211.1 and the 4th servo valve 211.2 provides high-precision control oil.The P mouth of the 3rd servo valve 211.1 links to each other with the A mouth of the 5th hydraulic control one-way valve 213.1, and the T mouth links to each other with the oil return pipe T pipe of hydraulic oil source, and the A mouth links to each other with the A mouth of the 7th hydraulic control one-way valve 213.3.The P mouth of the 4th servo valve 211.2 links to each other with the A mouth of the 6th hydraulic control one-way valve 213.2, and the T mouth links to each other with the oil return pipe T pipe of hydraulic oil source, and the A mouth links to each other with the A mouth of the 8th hydraulic control one-way valve 213.4.The P mouth of second solenoid directional control valve 212 links to each other with oil sources hydraulic oil P pipe, and the B mouth links to each other with the X mouth of the 6th hydraulic control one-way valve 213.2, the X mouth of the 8th hydraulic control one-way valve 213.4, the X mouth of second hydraulic control one-way valve 113.2 and the X mouth of the 4th hydraulic control one-way valve 113.4 respectively.The A1 mouth of the 5th hydraulic control one-way valve 213.1 links to each other with oil sources hydraulic oil P pipe, and the A mouth links to each other with the P mouth of the 3rd servo valve 211.1.The A1 mouth of the 6th hydraulic control one-way valve 213.2 links to each other with oil sources hydraulic oil P pipe, and the A mouth links to each other with the P mouth of the 4th servo valve 211.2.The A1 mouth of the 7th hydraulic control one-way valve 213.3 links to each other with the rodless cavity A mouth of second servo-cylinder 217, and the A mouth links to each other with the A mouth of the 3rd servo valve 211.1.The A1 mouth of the 8th hydraulic control one-way valve 213.4 links to each other with the rodless cavity A mouth of second servo-cylinder 217, and the A mouth links to each other with the A mouth of the 4th servo valve 211.2.The A mouth of second electromagnetic relief valve 215 links to each other with the rodless cavity A mouth of second servo-cylinder 217, and the B mouth links to each other with the oil return pipe T pipe of hydraulic oil source.The A mouth of second pressure-reducing valve 216 links to each other with the rod chamber B mouth of second servo-cylinder 217, and the B mouth links to each other with oil sources hydraulic oil P pipe, the T mouth links to each other with the oil return pipe T pipe of hydraulic oil source.The pressure tap of second pressure sensor 8.3 links to each other with the rodless cavity A mouth of servo-cylinder.The pressure tap of the 3rd pressure sensor 218.1 links to each other with the rod chamber B mouth of second servo-cylinder 217.Second displacement transducer 219 is installed on the fore side HGC cylinder.The PS mouth of the second low pressure accumulator group 220 links to each other with the rod chamber B mouth of second servo-cylinder 217, and the T mouth links to each other with the oil return pipe T pipe of hydraulic oil source.The P3 mouth of the second high pressure accumulator group 221 links to each other with the A1 mouth of the 5th hydraulic control one-way valve 213.1 and the A1 mouth of the 6th hydraulic control one-way valve 213.2.
In actual applications, when roll rising/decline, second solenoid directional control valve 212, first servo valve 111.1, the 3rd servo valve 211.1 are opened earlier, realize the control of fluid low discharge; When the oily flow of system requirements surpassed the set maximum stream flow of first servo valve 111.1, the 3rd servo valve 211.1, first solenoid directional control valve 112, second servo valve 111.2, the 4th servo valve 211.2 were opened, and realize the control of the big flow of fluid; When system requirements rises topping roll fast, the electromagnet a of the electromagnet a of first electromagnetic relief valve 115, second electromagnetic relief valve 215 gets electric, and the fluid in the rodless cavity of servo-cylinder 117 of winning (transmission side HGC oil cylinder) and second servo-cylinder 217 (fore side HGC oil cylinder) is discharged rapidly.In said process, the first low pressure accumulator group 120, the second low pressure accumulator group 220, the first high pressure accumulator group 121, the second high pressure accumulator group 221 mainly act as the absorption hydraulic shock.
Fig. 3 (Fig. 3 A to Fig. 3 H) and Fig. 4 (Fig. 4 A to Fig. 4 C) are the auxiliary hydraulic pressure control system schematic diagram of casting and rolling machine of the present utility model.This auxiliary hydraulic pressure control system is put by a cover top roll compensating cylinder control system, and connects spindle balance cylinder control system, a cover bottom spindle compensating cylinder control system, a cover upper joint-shaft and hold hydraulic cylinder control system, a cover bottom spindle tightly and hold hydraulic cylinder control system, tightly and put roll axial locking control system, a cover bottom roll axial locking control system, two cover side planishers locking hydraulic cylinders control systems, a cover track lift cylinders control system and a cover roll change cylinder control system and form.
Wherein, the P1 pipe of the first auxiliary hydraulic system valve platform links to each other with the P1 pipe of auxiliary hydraulic system accumulator group, and the T pipe links to each other with the oil return pipe T pipe of hydraulic oil source, the L pipe links to each other with the drain mast L pipe of hydraulic oil source.The P2 pipe of the second auxiliary hydraulic system valve platform links to each other with the P2 pipe of auxiliary hydraulic system accumulator group, and the T pipe links to each other with the oil return pipe T pipe of hydraulic oil source, the L pipe links to each other with the drain mast L pipe of hydraulic oil source.The P pipe oil sources hydraulic oil P pipe of auxiliary hydraulic system accumulator group links to each other, and the T pipe links to each other with the oil return pipe T pipe of hydraulic oil source.
With reference to figure 3A, upper joint-shaft hold tightly hydraulic control system mainly by: first check valve 311, the first 3-position 4-way solenoid directional control valve 312, first stacking type hydraulic control check valve 313, the first superposing type Double throttle check valve 314, first pressure switch 315, second pressure switch 316, first oil cylinder 317 and second oil cylinder 318 are formed.Wherein, the P mouth of the first 3-position 4-way solenoid directional control valve 312 links to each other with the P1 pipe of the first auxiliary hydraulic system valve platform, its T pipe links to each other with the T pipe of the first auxiliary hydraulic system valve platform, its A mouth links to each other with the A mouth of first stacking type hydraulic control check valve 313, and its B mouth links to each other with the B mouth of first stacking type hydraulic control check valve 313.The A mouth of first stacking type hydraulic control check valve 313 links to each other with the A mouth of the first 3-position 4-way solenoid directional control valve 312, its B mouth links to each other with the B mouth of the first 3-position 4-way solenoid directional control valve 312, its A1 mouth links to each other with the A mouth of the first superposing type Double throttle check valve 314, and its B1 mouth links to each other with the B mouth of the first superposing type Double throttle check valve 314.The A mouth of the first superposing type Double throttle check valve 314 links to each other with the A1 mouth of first stacking type hydraulic control check valve 313, its B mouth links to each other with the B1 mouth of first stacking type hydraulic control check valve 313, its A1 mouth links to each other with the A mouth of first oil cylinder 317 with second oil cylinder 318 respectively, and its B1 mouth links to each other with the B mouth of first oil cylinder 317 with second oil cylinder 318 respectively.The pressure tap of first pressure switch 315 links to each other with the A mouth of first oil cylinder 317 with second oil cylinder 318 respectively, and the pressure tap of second pressure switch 316 links to each other with the B mouth of first oil cylinder 317 with second oil cylinder 318 respectively.The first 3-position 4-way solenoid directional control valve 312 and first pressure switch 315, second pressure switch 316 carry out interlocked control.And first pressure switch 315, second pressure switch 316 detect the rod chamber of first oil cylinder 317 and second oil cylinder 318, the pressure of rodless cavity respectively.
In actual applications, the electromagnet DT1A of the first 3-position 4-way solenoid directional control valve 312 gets, first oil cylinder 317 and second oil cylinder 318 are held tightly, first pressure switch 315 detects the concurrent signal of enclasping pressure of setting, expression pressure is normal, the work that can interlock with it, otherwise expression pressure anomaly, the work of not interlocking with it.When the electromagnet DT1B of the first 3-position 4-way solenoid directional control valve 312 gets, first oil cylinder 317 and second oil cylinder 318 unclamp, what second pressure switch 316 detected setting unclamps the concurrent signal of pressure, expression pressure is normal, the work that can interlock with it, otherwise the expression pressure anomaly, the work of not interlocking with it.
With reference to figure 3B, bottom spindle hold tightly hydraulic control system mainly by: second check valve 321, the second 3-position 4-way solenoid directional control valve 322, second stacking type hydraulic control check valve 323, the second superposing type Double throttle check valve 324, the 3rd pressure switch 325, the 4th pressure switch 326, the 3rd oil cylinder 327 and the 4th oil cylinder 328 are formed.Wherein, the P mouth of the second 3-position 4-way solenoid directional control valve 322 links to each other with the P1 pipe of the first auxiliary hydraulic system valve platform, its T pipe links to each other with the T pipe of the first auxiliary hydraulic system valve platform, its A mouth links to each other with the A mouth of second stacking type hydraulic control check valve 323, and its B mouth links to each other with the B mouth of second stacking type hydraulic control check valve 323.The A mouth of second stacking type hydraulic control check valve 323 links to each other with the A mouth of the second 3-position 4-way solenoid directional control valve 322, its B mouth links to each other with the B mouth of the second 3-position 4-way solenoid directional control valve 322, its A1 mouth links to each other with the A mouth of the second superposing type Double throttle check valve 324, and 1 mouthful of B mouth with the second superposing type Double throttle check valve 324 of its B links to each other.The A mouth of the second superposing type Double throttle check valve 324 links to each other with the A1 mouth of second stacking type hydraulic control check valve 323, its B mouth links to each other with the B1 mouth of second stacking type hydraulic control check valve 323, its A1 mouth links to each other with the A mouth of the 3rd oil cylinder 327 with the 4th oil cylinder 328 respectively, and its B1 mouth links to each other with the B mouth of the 3rd oil cylinder 327 with the 4th oil cylinder 328 respectively.The pressure tap of the 3rd pressure switch 325 links to each other with the A mouth of the 3rd oil cylinder 327 with the 4th oil cylinder 328 respectively, and the pressure tap of the 4th pressure switch 326 links to each other with the B mouth of the 3rd oil cylinder 327 with the 4th oil cylinder 328 respectively.The second 3-position 4-way solenoid directional control valve 322 and the 3rd pressure switch 325, the 4th pressure switch 326 carry out interlocked control.And the 3rd pressure switch 325, the 4th pressure switch 326 detect the rod chamber of the 3rd oil cylinder 327 and the 4th oil cylinder 328, the pressure of rodless cavity respectively.
In actual applications, the electromagnet DT2A of the second 3-position 4-way solenoid directional control valve 322 gets, the 3rd oil cylinder 327 and the 4th oil cylinder 328 are held tightly, the 3rd pressure switch 325 detects the concurrent signal of enclasping pressure of setting, expression pressure is normal, the work that can interlock with it, otherwise expression pressure anomaly, the work of not interlocking with it.When the electromagnet DT2B of the second 3-position 4-way solenoid directional control valve 322 gets, the 3rd oil cylinder 327 and the 4th oil cylinder 328 unclamp, what the 4th pressure switch 326 detected setting unclamps the concurrent signal of pressure, expression pressure is normal, the work that can interlock with it, otherwise the expression pressure anomaly, the work of not interlocking with it.
With reference to figure 3C, topping roll axial locking hydraulic control system mainly by: the 3rd check valve 331, the 3rd 3-position 4-way solenoid directional control valve 332, the 3rd stacking type hydraulic control check valve 333, the 3rd superposing type Double throttle check valve 334, the 5th pressure switch 335, the 6th pressure switch 336, the 5th oil cylinder 337 and the 6th oil cylinder 338 are formed.Wherein, the P mouth of the 3rd 3-position 4-way solenoid directional control valve 332 links to each other with the P1 pipe of the first auxiliary hydraulic system valve platform, its T pipe links to each other with the T pipe of the first auxiliary hydraulic system valve platform, its A mouth links to each other with the A mouth of the 3rd stacking type hydraulic control check valve 333, and its B mouth links to each other with the B mouth of the 3rd stacking type hydraulic control check valve 333.The A mouth of the 3rd stacking type hydraulic control check valve 333 links to each other with the A mouth of the 3rd 3-position 4-way solenoid directional control valve 332, its B mouth links to each other with the B mouth of the 3rd 3-position 4-way solenoid directional control valve 332, its A1 mouth links to each other with the A mouth of the 3rd superposing type Double throttle check valve 334, and its B1 mouth links to each other with the B mouth of the 3rd superposing type Double throttle check valve 334.The A mouth of the 3rd superposing type Double throttle check valve 334 links to each other with the A1 mouth of the 3rd stacking type hydraulic control check valve 333, its B mouth links to each other with the B1 mouth of the 3rd stacking type hydraulic control check valve 333, its A1 mouth links to each other with the A mouth of the 5th oil cylinder 337 with the 6th oil cylinder 338 respectively, and its B1 mouth links to each other with the B mouth of the 5th oil cylinder 337 with the 6th oil cylinder 338 respectively.The pressure tap of the 5th pressure switch 335 links to each other with the A mouth of the 5th oil cylinder 337 with the 6th oil cylinder 338 respectively, and the pressure tap of the 6th pressure switch 336 links to each other with the B mouth of the 5th oil cylinder 337 with the 6th oil cylinder 338 respectively.The 3rd 3-position 4-way solenoid directional control valve 332 and the 5th pressure switch 335, the 6th pressure switch 336 carry out interlocked control.And the 5th pressure switch 335, the 6th pressure switch 336 detect the rod chamber of the 5th oil cylinder 337 and the 6th oil cylinder 338, the pressure of rodless cavity respectively.
In actual applications, the electromagnet DT3A of the 3rd 3-position 4-way solenoid directional control valve 332 gets, the 5th oil cylinder 337 and the 6th oil cylinder 338 are held tightly, the 5th pressure switch 335 detects the concurrent signal of enclasping pressure of setting, expression pressure is normal, the work that can interlock with it, otherwise expression pressure anomaly, the work of not interlocking with it.When the electromagnet DT3B of the 3rd 3-position 4-way solenoid directional control valve 332 gets, the 5th oil cylinder 337 and the 6th oil cylinder 338 unclamp, what the 6th pressure switch 336 detected setting unclamps the concurrent signal of pressure, expression pressure is normal, the work that can interlock with it, otherwise the expression pressure anomaly, the work of not interlocking with it.
With reference to figure 3D, bottom roll axial locking hydraulic control system mainly by: the 4th check valve 341, the 4th 3-position 4-way solenoid directional control valve 342, the 4th stacking type hydraulic control check valve 343, the 4th superposing type Double throttle check valve 344, the 7th pressure switch 345, the 8th pressure switch 346, the 7th oil cylinder 347 and the 8th oil cylinder 348 are formed.Wherein, the P mouth of the 4th 3-position 4-way solenoid directional control valve 342 links to each other with the P1 pipe of the first auxiliary hydraulic system valve platform, its T pipe links to each other with the T pipe of the first auxiliary hydraulic system valve platform, its A mouth links to each other with the A mouth of the 4th stacking type hydraulic control check valve 343, and its B mouth links to each other with the B mouth of the 4th stacking type hydraulic control check valve 343.The A mouth of the 4th stacking type hydraulic control check valve 343 links to each other with the A mouth of the 4th 3-position 4-way solenoid directional control valve 342, its B mouth links to each other with the B mouth of the 4th 3-position 4-way solenoid directional control valve 342, its A1 mouth links to each other with the A mouth of the 4th superposing type Double throttle check valve 344, and its B1 mouth links to each other with the B mouth of the 4th superposing type Double throttle check valve 344.The A mouth of the 4th superposing type Double throttle check valve 344 links to each other with the A1 mouth of the 4th stacking type hydraulic control check valve 343, its B mouth links to each other with the B1 mouth of the 4th stacking type hydraulic control check valve 343, its A1 mouth links to each other with the A mouth of the 7th oil cylinder 347 with the 8th oil cylinder 348 respectively, and its B1 mouth links to each other with the B mouth of the 7th oil cylinder 347 with the 8th oil cylinder 348 respectively.The pressure tap of the 7th pressure switch 345 links to each other with the A mouth of the 7th oil cylinder 347 with the 8th oil cylinder 348 respectively, and the pressure tap of the 8th pressure switch 346 links to each other with the B mouth of the 7th oil cylinder 347 with the 8th oil cylinder 348 respectively.The 4th 3-position 4-way solenoid directional control valve 342 and the 7th pressure switch 345, the 8th pressure switch 346 carry out interlocked control.And the 7th pressure switch 345, the 8th pressure switch 346 detect the rod chamber of the 7th oil cylinder 347 and the 8th oil cylinder 348, the pressure of rodless cavity respectively.
In actual applications, the electromagnet DT4A of the 4th 3-position 4-way solenoid directional control valve 342 gets, the 7th oil cylinder 347 and the 8th oil cylinder 348 are held tightly, the 7th pressure switch 345 detects the concurrent signal of enclasping pressure of setting, expression pressure is normal, the work that can interlock with it, otherwise expression pressure anomaly, the work of not interlocking with it.When the electromagnet DT4B of the 4th 3-position 4-way solenoid directional control valve 342 gets, the 7th oil cylinder 347 and the 8th oil cylinder 348 unclamp, what the 8th pressure switch 346 detected setting unclamps the concurrent signal of pressure, expression pressure is normal, the work that can interlock with it, otherwise the expression pressure anomaly, the work of not interlocking with it.
With reference to figure 3E, first side planisher locking hydraulic control system mainly by: the 5th check valve 351, the 5th 3-position 4-way solenoid directional control valve 352, the 5th stacking type hydraulic control check valve 353, the 5th superposing type Double throttle check valve 354, the 9th pressure switch 355, the tenth pressure switch 356, the 9th oil cylinder 357 and the tenth oil cylinder 358 are formed.Wherein, the P mouth of the 5th 3-position 4-way solenoid directional control valve 352 links to each other with the P1 pipe of the first auxiliary hydraulic system valve platform, its T pipe links to each other with the T pipe of the first auxiliary hydraulic system valve platform, its A mouth links to each other with the A mouth of the 5th stacking type hydraulic control check valve 353, and its B mouth links to each other with the B mouth of the 5th stacking type hydraulic control check valve 353.The A mouth of the 5th stacking type hydraulic control check valve 353 links to each other with the A mouth of the 5th 3-position 4-way solenoid directional control valve 352, its B mouth links to each other with the B mouth of the 5th 3-position 4-way solenoid directional control valve 352, and its A1 mouth links to each other with the A mouth of the 5th superposing type Double throttle check valve 354, its B1 mouth links to each other with the B mouth of the 5th superposing type Double throttle check valve 354.The A mouth of the 5th superposing type Double throttle check valve 354 links to each other with the A1 mouth of the 5th stacking type hydraulic control check valve 353, its B mouth links to each other with the B1 mouth of the 5th stacking type hydraulic control check valve 353, its A1 mouth links to each other with the A mouth of the 9th oil cylinder 357 with the tenth oil cylinder 358 respectively, and its B1 mouth links to each other with the B mouth of the 9th oil cylinder 357 with the tenth oil cylinder 358 respectively.The pressure tap of the 9th pressure switch 355 links to each other with the A mouth of the 9th oil cylinder 357 with the tenth oil cylinder 358 respectively, and the pressure tap of the tenth pressure switch 356 links to each other with the B mouth of the 9th oil cylinder 357 with the tenth oil cylinder 358 respectively.The 5th 3-position 4-way solenoid directional control valve 352 and the 9th pressure switch 355, the tenth pressure switch 356 carry out interlocked control.And the 9th pressure switch 355, the tenth pressure switch 356 detect the rod chamber of the 9th oil cylinder 357 and the tenth oil cylinder 358, the pressure of rodless cavity respectively.
In actual applications, when the electromagnet DT5A of the 5th 3-position 4-way solenoid directional control valve 352 gets, the 9th oil cylinder 357 and the tenth oil cylinder 358 are held tightly, the 9th pressure switch 355 detects the concurrent signal of enclasping pressure of setting, expression pressure is normal, the work that can interlock with it, otherwise expression pressure anomaly, the work of not interlocking with it.When the electromagnet DT5B of the 5th 3-position 4-way solenoid directional control valve 352 gets, the 9th oil cylinder 357 and the tenth oil cylinder 358 unclamp, what the tenth pressure switch 356 detected setting unclamps the concurrent signal of pressure, expression pressure is normal, the work that can interlock with it, otherwise the expression pressure anomaly, the work of not interlocking with it.
With reference to figure 3F, second side planisher locking hydraulic control system mainly by: the 6th check valve 361, the 6th 3-position 4-way solenoid directional control valve 362, the 6th stacking type hydraulic control check valve 363, the 6th superposing type Double throttle check valve the 364, the 11 pressure switch the 365, the 12 pressure switch the 366, the 11 oil cylinder 367 and the 12 oil cylinder 368 are formed.Wherein, the P mouth of the 6th 3-position 4-way solenoid directional control valve 362 links to each other with the P1 pipe of the first auxiliary hydraulic system valve platform, its T pipe links to each other with the T pipe of the first auxiliary hydraulic system valve platform, its A mouth links to each other with the A mouth of the 6th stacking type hydraulic control check valve 363, and its B mouth links to each other with the B mouth of the 6th stacking type hydraulic control check valve 363.The A mouth of the 6th stacking type hydraulic control check valve 363 links to each other with the A mouth of the 6th 3-position 4-way solenoid directional control valve 362, its B mouth links to each other with the B mouth of the 6th 3-position 4-way solenoid directional control valve 362, and its A1 mouth links to each other with the A mouth of the 6th superposing type Double throttle check valve 364, its B1 mouth links to each other with the B mouth of the 6th superposing type Double throttle check valve 364.The A mouth of the 6th superposing type Double throttle check valve 364 links to each other with the A1 mouth of the 6th stacking type hydraulic control check valve 363, its B mouth links to each other with the B1 mouth of the 6th stacking type hydraulic control check valve 363, its A1 mouth links to each other with the A mouth of the 11 oil cylinder 367 and oil cylinder 368, and its B1 mouth links to each other with the B mouth of the 11 oil cylinder 367 and the 12 oil cylinder 368 respectively.The pressure tap of the 11 pressure switch 365 links to each other with the A mouth of the 11 oil cylinder 367 and the 12 oil cylinder 368 respectively, and the pressure tap of the 12 pressure switch 366 links to each other with the B mouth of the 11 oil cylinder 367 and the 12 oil cylinder 368 respectively.The 6th 3-position 4-way solenoid directional control valve 362 and the 11 pressure switch the 365, the 12 pressure switch 366 carry out interlocked control.And the 11 pressure switch the 365, the 12 pressure switch 366 detects the 11 oil cylinder 367 and the rod chamber of the 12 oil cylinder 368, the pressure of rodless cavity respectively.
In actual applications, when the electromagnet DT6A of the 6th 3-position 4-way solenoid directional control valve 362 gets, the 11 oil cylinder 367 and the 12 oil cylinder 368 are held tightly, the 11 pressure switch 365 detects the concurrent signal of enclasping pressure of setting, expression pressure is normal, the work that can interlock with it, otherwise expression pressure anomaly, the work of not interlocking with it.When the electromagnet DT6B of the 6th 3-position 4-way solenoid directional control valve 362 gets, the 11 oil cylinder 367 and the 12 oil cylinder 368 unclamp, what the 12 pressure switch 366 detected setting unclamps the concurrent signal of pressure, expression pressure is normal, the work that can interlock with it, otherwise the expression pressure anomaly, the work of not interlocking with it.
With reference to figure 3G, roll change hydraulic cylinder hydraulic control system mainly by: the 7th check valve 371, electro-hydraulic proportion reversing valve 372, pressure compensator 373, the 7th stacking type hydraulic control check valve 374, hydraulic pressure bridge circuit 375, overflow valve 376, roll change oil cylinder 377, first travel switch 378.1, second travel switch 378.2, third trip switch 378.3 and fourth line journey switch 378.4 are formed.Wherein, the P mouth of electro-hydraulic proportion reversing valve 372 links to each other with the P1 mouth of pressure compensator 373, and the T mouth links to each other with the T pipe of the 1st page of auxiliary hydraulic system valve platform one Fig. 2, and the A mouth links to each other with the A1 mouth of pressure compensator 373, and the B mouth links to each other with the B1 mouth of pressure compensator 373.The P mouth of pressure compensator 373 links to each other with the P1 pipe of the first auxiliary hydraulic system valve platform, its T mouth links to each other with the T pipe of the first auxiliary hydraulic system valve platform, its A1 mouth links to each other with the A mouth of electro-hydraulic proportion reversing valve 372, its B1 mouth links to each other with the B mouth of electro-hydraulic proportion reversing valve 372, its A mouth links to each other with the A mouth of the 7th stacking type hydraulic control check valve 374, and its B mouth links to each other with the B mouth of the 7th stacking type hydraulic control check valve 374.Pressure compensator 373 be superimposed upon electro-hydraulic proportion reversing valve 372 below; The 7th stacking type hydraulic control check valve 374 be superimposed upon pressure compensator 373 below; Hydraulic pressure bridge circuit 375 is connected with rod chamber, the rodless cavity of roll change oil cylinder 377 respectively.First travel switch 378.1, second travel switch 378.2, third trip switch 378.3 and fourth line journey switch 378.4 carry out interlocked control with electro-hydraulic proportion reversing valve 372 respectively.
In actual applications, the electromagnet DT7A of electro-hydraulic proportion reversing valve 372 gets electric, and the cylinder bar of roll change oil cylinder 377 will stretch out according to the rate curve of system's setting, and roll is advanced milling train; The electromagnet DT7B of electro-hydraulic proportion reversing valve 372 gets electric, and the cylinder bar of roll change oil cylinder 377 will be withdrawn according to the rate curve that system is provided with, and roll is pulled out milling train.First overflow valve 376 plays the effect of safe overflow in the oil cylinder motion, avoid system too high pressure peak to occur.
With reference to figure 3H, the track lifting hydraulic control system mainly by: the 8th check valve 381, the 7th 3-position 4-way solenoid directional control valve 382, the 8th stacking type hydraulic control check valve 383, balanced valve the 384, the 13 pressure switch the 385, the 14 pressure switch 386, first cowling panel 387.1, second cowling panel 387.2, first flow speed control valve 388.1, second flow speed control valve the 388.2, the 13 oil cylinder 389.1 and the 14 oil cylinder 389.2 are formed.Wherein, the P mouth of the 7th 3-position 4-way solenoid directional control valve 382 links to each other with the P1 pipe of the first auxiliary hydraulic system valve platform, its T pipe links to each other with the T pipe of the first auxiliary hydraulic system valve platform, its A mouth links to each other with the A mouth of the 8th stacking type hydraulic control check valve 383, and the B mouth links to each other with the B mouth of the 8th stacking type hydraulic control check valve 383.The A mouth of the 8th stacking type hydraulic control check valve 383 links to each other with the A mouth of the 7th 3-position 4-way solenoid directional control valve 382, its B mouth links to each other with the B mouth of the 7th 3-position 4-way solenoid directional control valve 382, its A1 mouth links to each other with the A mouth of balanced valve 384, and its B1 mouth links to each other with the rod chamber B mouth of the 13 oil cylinder 389.1 and the rod chamber B mouth of the 14 oil cylinder 25.2 with the X mouth of balanced valve 384.The A mouth of balanced valve 384 links to each other with the A1 mouth of the 8th stacking type hydraulic control check valve 383, its B mouth links to each other with the A1 mouth of cowling panel 22.1 and the A1 mouth of cowling panel 22.2, and its X mouth links to each other with the B1 mouth of the 8th stacking type hydraulic control check valve 383, the rod chamber B mouth of the 13 oil cylinder 389.1 and the rod chamber B mouth of the 14 oil cylinder 389.2 respectively.First flow speed control valve 23.1 is superimposed upon on first cowling panel 387.1.The A1 mouth of first cowling panel 387.1 links to each other with the B mouth of balanced valve 384, and the B1 mouth of first cowling panel 387.1 links to each other with the rodless cavity A mouth of the 13 oil cylinder 389.1.Second flow speed control valve 388.1 is superimposed upon on second cowling panel 387.2.The A1 mouth of second cowling panel 387.2 links to each other with the B mouth of balanced valve 384, and the B1 mouth of second cowling panel 387.2 links to each other with the rodless cavity A mouth of the 14 oil cylinder 389.2.The pressure tap of the 13 pressure switch 385 is connected between the A1 mouth of the B mouth of balanced valve 384 and first cowling panel 387.1.The pressure tap of the 14 pressure switch 386 is connected between the rod chamber B mouth of rod chamber B mouth, the 14 oil cylinder 389.2 of the B1 mouth of the 8th stacking type hydraulic control check valve 383 and the 13 oil cylinder 389.1.The 13 pressure switch the 385, the 14 pressure switch 386 detects the 13 oil cylinder 389.1 and the rod chamber of the 14 oil cylinder 389.2, the pressure of rodless cavity respectively.
In actual applications, when the electromagnet DT8A of the 7th 3-position 4-way solenoid directional control valve 382 gets, the track lifting, the 13 pressure switch 382 detects the concurrent signal of preset pressure value, expression pressure is normal, the work that can interlock with it, otherwise expression pressure anomaly, the work of not interlocking with it.When the electromagnet DT8B of solenoid directional control valve 382 gets electricly, track descends, and the 14 pressure switch 386 detects the concurrent signal of preset pressure value, and expression pressure is normal, the work that can interlock with it, otherwise expression pressure anomaly, the work of not interlocking with it.First flow speed control valve 388.1 and second flow speed control valve 388.2 are used to guarantee being synchronized with the movement of the 13 oil cylinder 389.1 and the 14 oil cylinder 389.2.Balanced valve 384 is used to guarantee that the 13 oil cylinder 389.1 and the 14 oil cylinder 389.2 can steadily descend.
With reference to figure 4A, top working roll balanced hydraulic control system mainly is made up of: first throttle valve 411, the first two four-way electromagnetic reversing valves 412, the second two four-way electromagnetic reversing valves 413, the 9th hydraulic control one-way valve 414, second overflow valve the 415, the 15 pressure switch 416 and first plunger cases 417.Wherein, the P mouth of the first two four-way electromagnetic reversing valves 412 links to each other with the P2 of second auxiliary hydraulic system valve platform pipe, and its T mouth links to each other with the B mouth of first throttle valve 411, and its B mouth links to each other with the P1 mouth of the 9th hydraulic control one-way valve 414.The T pipe of the A mouth of first throttle valve 411 and the second auxiliary hydraulic system valve platform links to each other, and its B mouth links to each other with the T mouth of the first two four-way electromagnetic reversing valves 412.The P mouth of the second two four-way electromagnetic reversing valves 413 links to each other with the P2 of second auxiliary hydraulic system valve platform pipe, and its T mouth is managed with the T of the second auxiliary hydraulic system valve platform and linked to each other, and its B mouth links to each other with the X mouth of the 9th hydraulic control one-way valve 414.The P1 mouth of the 9th hydraulic control one-way valve 414 links to each other with the B mouth of the first two four-way electromagnetic reversing valves 412, and its P2 mouth links to each other with the rodless cavity of first plunger case 417.The B mouth of second overflow valve 415 is connected between the rodless cavity of the P2 mouth of the 9th hydraulic control one-way valve 414 and first plunger case 417, and its A mouth links to each other with the T pipe of the second auxiliary hydraulic system valve platform.The pressure interface of the 15 pressure switch 416 links to each other with the B mouth of second overflow valve 4155.The 15 pressure switch 416 is used to detect the equalizing pressure of first plunger case 417.
In actual applications, when the electromagnet DT9A of the first two four-way electromagnetic reversing valves 412 gets, the top working roll balance hydraulic cylinder rises, the 15 pressure switch 416 detects the concurrent signal of preset pressure value, expression pressure is normal, the work that can interlock with it, otherwise expression pressure anomaly, the work of not interlocking with it.Get electricly when the electromagnet DT9B of the first two four-way electromagnetic reversing valves 412 gets electromagnet DT10 electric, the second two four-way electromagnetic reversing valves 413, the 9th hydraulic control one-way valve 414 is opened, and the top working roll balance hydraulic cylinder descends.Second overflow valve 415 plays the effect of safe overflow in 417 motions of first plunger case, avoid system too high pressure peak to occur.First throttle valve 411 guarantees that first plunger case 417 steadily descends.
With reference to figure 4B, upper joint-shaft balanced hydraulic control system mainly by: the 422, the 4 two four-way electromagnetic reversing valve of the 421, the 3 two four-way electromagnetic reversing valve of second choke valve 423, the tenth hydraulic control one-way valve 424, the 3rd overflow valve the 425, the 16 pressure switch 426, second plunger case 427 and the 3rd plunger case 428 are formed.Wherein, the P mouth of the 3 two four-way electromagnetic reversing valve 422 links to each other with the P2 pipe of the second auxiliary hydraulic system valve platform, and its T mouth links to each other with the B mouth of second choke valve 421, and its B mouth links to each other with the P1 mouth of the tenth hydraulic control one-way valve 424.The A mouth of second choke valve 421 links to each other with the T pipe of the second auxiliary hydraulic system valve platform, and its B mouth links to each other with the T mouth of the 3 two four-way electromagnetic reversing valve 422.The P mouth of the 4 two four-way electromagnetic reversing valve 423 links to each other with the P2 pipe of the second auxiliary hydraulic system valve platform, and its T mouth links to each other with the T pipe of the second auxiliary hydraulic system valve platform, and its B mouth links to each other with the X mouth of the tenth hydraulic control one-way valve 424.The P1 mouth of the tenth hydraulic control one-way valve 424 links to each other with the B mouth of the 3 two four-way electromagnetic reversing valve 422, and its P2 mouth links to each other with the rodless cavity of second plunger case 427 and the 3rd plunger case 428.The B mouth of the 3rd overflow valve 425 is connected between the rodless cavity of the P2 mouth of the tenth hydraulic control one-way valve 424 and second plunger case 427 and the 3rd plunger case 428, and its A mouth links to each other with the T pipe of the second auxiliary hydraulic system valve platform.The pressure interface of the 16 pressure switch 426 links to each other with the B mouth of the 3rd overflow valve 425.The 16 pressure switch 426 is used for detecting respectively the equalizing pressure of second plunger case 427 and the 3rd plunger case 428.
In actual applications, the electromagnet DT11A of the 3 two four-way electromagnetic reversing valve 422 gets, the upper joint-shaft balance hydraulic cylinder rises, when the 16 pressure switch 426 detects the concurrent signal of preset pressure value, expression pressure is normal, the work that can interlock with it, otherwise expression pressure anomaly, the work of not interlocking with it.The electromagnet DT11B of the 3 two four-way electromagnetic reversing valve 422 gets electromagnet DT12 electric, the 4 two four-way electromagnetic reversing valve 423 and gets electricly, and the tenth hydraulic control one-way valve 424 is opened, and the upper joint-shaft balance hydraulic cylinder descends.The 3rd overflow valve 425 plays the effect of safe overflow in the oil cylinder motion, avoid system too high pressure peak to occur.Second choke valve 421 guarantees that oil cylinder steadily descends.
With reference to figure 4C, bottom spindle balanced hydraulic control system mainly by: the 432, the 6 two four-way electromagnetic reversing valve of the 431, the 5 two four-way electromagnetic reversing valve of the 3rd choke valve the 433, the 11 hydraulic control one-way valve 434, the 4th overflow valve the 435, the 17 pressure switch 436, the 4th plunger case 437 and the 5th plunger case 438 are formed.Wherein, the P mouth of the 5 two four-way electromagnetic reversing valve 432 links to each other with the P2 pipe of the second auxiliary hydraulic system valve platform, and its T mouth links to each other with the B mouth of the 3rd choke valve 431, and its B mouth links to each other with the P1 mouth of the 11 hydraulic control one-way valve 434.The A mouth of the 3rd choke valve 431 links to each other with the T pipe of the second auxiliary hydraulic system valve platform, and its B mouth links to each other with the T mouth of the 5 two four-way electromagnetic reversing valve 432.The P mouth of the 6 two four-way electromagnetic reversing valve 433 links to each other with the P2 pipe of the second auxiliary hydraulic system valve platform, and its T mouth links to each other with the T pipe of the second auxiliary hydraulic system valve platform, and its B mouth links to each other with the X mouth of the 11 hydraulic control one-way valve 434.The P1 mouth of the 11 hydraulic control one-way valve 434 links to each other with the B mouth of the 5 two four-way electromagnetic reversing valve 432, and its P2 mouth links to each other with the rodless cavity of the 4th plunger case 437 and the 5th plunger case 438.The B mouth of the 4th overflow valve 435 is connected between the rodless cavity of the P2 mouth of the 11 hydraulic control one-way valve 434 and the 4th plunger case 437 and the 5th plunger case 438, and its A mouth links to each other with the T pipe of the second auxiliary hydraulic system valve platform.The pressure interface of the 17 pressure switch 436 links to each other with the B mouth of the 4th overflow valve 435.The 17 pressure switch 431 detects the equalizing pressure of the 4th plunger case 437 and the 5th plunger case 438 respectively.
In actual applications, the electromagnet DT13A of the 5 two four-way electromagnetic reversing valve 432 gets, the bottom spindle balance hydraulic cylinder rises, when the 17 pressure switch 436 detects the concurrent signal of preset pressure value, expression pressure is normal, the work that can interlock with it, otherwise expression pressure anomaly, the work of not interlocking with it.The electromagnet DT14 that gets electric and the 6 two four-way electromagnetic reversing valve 433 as the electromagnet DT13B of the 5 two four-way electromagnetic reversing valve 432 gets electric, and the 11 hydraulic control one-way valve 434 is opened, and the bottom spindle balance hydraulic cylinder descends.The 4th overflow valve 435 plays the effect of safe overflow in the oil cylinder motion, avoid system too high pressure peak to occur.The 3rd choke valve 431 guarantees that oil cylinder steadily descends.
In addition, the hydraulic control system according to the utility model embodiment also comprises: the first swing fan-shaped section hydraulic control system and the second swing fan-shaped section hydraulic control system.
With reference to figure 5, Fig. 5 is the hydraulic control system schematic diagram of the utility model swing fan-shaped section.The hydraulic control system of swing fan-shaped section comprises two cover plunger cylinder control systems, two cover plunger cylinder control systems can drive the swing fan-shaped section before and after the above-mentioned casting and rolling machine respectively, make the swing fan-shaped section to freely swing around separately fulcrum, with the work of fine cooperation casting and rolling machine according to actual conditions.Wherein, the P1 pipe of swing fan-shaped section hydraulic system valve platform links to each other with the P1 pipe of auxiliary hydraulic system accumulator group.
As shown in Figure 5, the first swing fan-shaped section hydraulic control system mainly by: the 512, the 8 two four-way electromagnetic reversing valve of the 511, the 7 two four-way electromagnetic reversing valve of the 4th choke valve the 513, the 12 hydraulic control one-way valve 514, the 5th overflow valve the 515, the 18 pressure switch 516, the 6th plunger case 517 and the 7th plunger case 518 are formed.Wherein, the P mouth of the 7 two four-way electromagnetic reversing valve 512 links to each other with the P1 pipe of swing fan-shaped section hydraulic system valve platform, and its T mouth links to each other with the B mouth of the 4th choke valve 511, and its B mouth links to each other with the P1 mouth of the 12 hydraulic control one-way valve 514.The A mouth of the 4th choke valve 511 and swing fan-shaped section hydraulic system valve platform the T pipe link to each other, its B mouth links to each other with the T mouth of the 7 two four-way electromagnetic reversing valve 512.The P mouth of the 8 two four-way electromagnetic reversing valve 513 links to each other with the P2 pipe of swing fan-shaped section hydraulic system valve platform, and its T mouth links to each other with the T pipe of swing fan-shaped section hydraulic system valve platform, and its B mouth links to each other with the X mouth of the 12 hydraulic control one-way valve 514.The P1 mouth of the 12 hydraulic control one-way valve 514 links to each other with the B mouth of the 7 two four-way electromagnetic reversing valve 512, and its P2 mouth links to each other with the rodless cavity of the 6th plunger case 517 and the 7th plunger case 518.The B mouth of overflow valve 9.1 is connected between the rodless cavity of the P2 mouth of the 12 hydraulic control one-way valve 514 and the 6th plunger case 517 and the 7th plunger case 518, and its A mouth links to each other with the T pipe of swing fan-shaped section hydraulic system valve platform.The pressure interface of the 18 pressure switch 516 links to each other with the B mouth of the 5th overflow valve 5151.The 18 pressure switch 516 detects the equalizing pressure of the 6th plunger case 517 and the 7th plunger case 518 respectively.
Continuation with reference to figure 5, the second swing fan-shaped section hydraulic control systems mainly by: the 522, the 12 four-way electromagnetic reversing valve of the 521, the 9 two four-way electromagnetic reversing valve of the 5th choke valve the 523, the 13 hydraulic control one-way valve 524, the 6th overflow valve the 525, the 19 pressure switch 526, the 8th plunger case 527 and the 9th plunger case 528 are formed.Wherein, the P mouth of the 9 two four-way electromagnetic reversing valve 522 links to each other with the P2 pipe of swing fan-shaped section hydraulic system valve platform, and its T mouth links to each other with the B mouth of the 5th choke valve 521, and its B mouth links to each other with the P1 mouth of hydraulic control one-way valve 8.2.The A mouth of the 5th choke valve 521 links to each other with the T pipe of swing fan-shaped section hydraulic system valve platform, and its B mouth links to each other with the T mouth of the 9 two four-way electromagnetic reversing valve 522.The P mouth of the 12 four-way electromagnetic reversing valve 523 links to each other with the P2 pipe of swing fan-shaped section hydraulic system valve platform, and the T mouth links to each other with the T pipe of swing fan-shaped section hydraulic system valve platform, and its B mouth links to each other with the X mouth of hydraulic control one-way valve 8.2.The P1 mouth of the 13 hydraulic control one-way valve 524 links to each other with the B mouth of the 9 two four-way electromagnetic reversing valve 522, and its P2 mouth links to each other with the rodless cavity of the 8th plunger case 527 and the 9th plunger case 528.The B mouth of the 6th overflow valve 525 is connected between the rodless cavity of the P2 mouth of the 13 hydraulic control one-way valve 524 and the 8th plunger case 527 and the 9th plunger case 528, and its A mouth links to each other with the T pipe of swing fan-shaped section hydraulic system valve platform.The pressure interface of the 19 pressure switch 526 links to each other with the B mouth of the 6th overflow valve 525.The 19 pressure switch 526 is used for detecting respectively the equalizing pressure of the 8th plunger case 527 and the 9th plunger case 528
In actual applications, the electromagnet DT15A of the 7 two four-way electromagnetic reversing valve 512 gets, the first swing fan-shaped section rises, when the 18 pressure switch 516 detects the concurrent signal of preset pressure value, expression pressure is normal, the work that can interlock with it, otherwise expression pressure anomaly, the work of not interlocking with it.The electromagnet DT16 that the electromagnet DT15B of the 7 two four-way electromagnetic reversing valve 512 gets electric and the 8 two four-way electromagnetic reversing valve 513 gets electric, and the 12 hydraulic control one-way valve 514 is opened, and the first swing fan-shaped section descends.The 5th overflow valve 515 plays the effect of safe overflow in the oil cylinder motion, avoid system too high pressure peak to occur.The 4th choke valve 511 guarantees that oil cylinder steadily descends.
When the electromagnet DT17A of the 9 two four-way electromagnetic reversing valve 522 gets electricly, the second swing fan-shaped section rises, and pressure switch 10.2 detects the concurrent signal of preset pressure value, expression pressure is normal, the work that can interlock with it, otherwise expression pressure anomaly, the work of not interlocking with it.The electromagnet DT18 that the electromagnet DT17B of the 9 two four-way electromagnetic reversing valve 522 gets electric and the 12 four-way electromagnetic reversing valve 523 gets electric, and the 13 hydraulic control one-way valve 524 is opened, and the second swing fan-shaped section descends.The 6th overflow valve 525 plays the effect of safe overflow in the oil cylinder motion, avoid system too high pressure peak to occur.The 5th choke valve 521 guarantees that oil cylinder steadily descends.
To sum up,, have following effect by technique scheme of the present utility model:
(1) hydraulic control system stable working, precision height; Simple and compact for structure, sturdy and durable, help enhancing productivity.
(2) hydraulic control system of casting and rolling machine can provide more accurate roll gap control, roll-force control and shorter response time for casting and rolling machine, helps improving slab quality and production efficiency.
(3) hydraulic control system of swing fan-shaped section can effectively be protected the fan-shaped section of casting and rolling machine front and back.
The above is embodiment of the present utility model only, is not limited to the utility model, and for a person skilled in the art, the utility model can have various changes and variation.All within spirit of the present utility model and principle, any modification of being done, be equal to replacement, improvement etc., all should be included within the claim scope of the present utility model.

Claims (15)

1. hydraulic control system is used to control the casting and rolling machine of free thickness slab continuous casting and rolling line, it is characterized in that, comprising:
The first roll depress oil cylinder control system, the second roll depress oil cylinder control system, upper joint-shaft is held hydraulic cylinder control system tightly, bottom spindle is held hydraulic cylinder control system tightly, topping roll axial locking control system, bottom roll axial locking control system, first side planisher locking hydraulic cylinder control system, second side planisher locking hydraulic cylinder control system, track lift cylinders control system, roll change cylinder control system, top roll compensating cylinder control system, upper joint-shaft compensating cylinder control system, bottom spindle compensating cylinder control system.
2. system according to claim 2 is characterized in that,
The described first roll depress oil cylinder control system comprises: first servo valve (111.1), second servo valve (111.2), first solenoid directional control valve (112), first hydraulic control one-way valve (113.1), second hydraulic control one-way valve (113.2), the 3rd hydraulic control one-way valve (113.3), the 4th hydraulic control one-way valve (113.4), first high pressure filter (114), first electromagnetic relief valve (115), first pressure-reducing valve (116), first servo-cylinder (117), first pressure sensor (118.1), second pressure sensor (118.2), first displacement transducer (119), the first low pressure accumulator group (120), the first high pressure accumulator group (121);
The described second roll depress oil cylinder control system comprises: the 3rd servo valve (211.1), the 4th servo valve (211.2), second solenoid directional control valve (212), the 5th hydraulic control one-way valve (213.1), the 6th hydraulic control one-way valve (213.2), the 7th hydraulic control one-way valve (213.3), the 8th hydraulic control one-way valve (213.4), second high pressure filter (214), second electromagnetic relief valve (215), second pressure-reducing valve (216), second servo-cylinder (217), the 3rd pressure sensor (218.1), the 4th pressure sensor (218.2), second displacement transducer (219), the second low pressure accumulator group (220), the second high pressure accumulator group (221);
Described first servo valve (111.1), described second servo valve (111.2) are formed the primary importance closed-loop control system with described first displacement transducer (119); Described first servo valve (111.1), described second servo valve (111.2) are formed the first pressure closed loop control system with described first pressure sensor (118.1), described second pressure sensor (118.2), described first pressure-reducing valve (116);
Described first solenoid directional control valve (112) control described second hydraulic control one-way valve (113.2), described the 4th hydraulic control one-way valve (113.4), described the 6th hydraulic control one-way valve (213.2), described the 8th hydraulic control one-way valve (213.4);
Described first pressure sensor (118.1), described second pressure sensor (118.2) detect the pressure of described first servo-cylinder (117) rodless cavity, rod chamber respectively;
Described the 3rd servo valve (211.1), described the 4th servo valve (211.2) are formed second place closed-loop control system with described second displacement transducer (219); Described the 3rd servo valve (211.1), described the 4th servo valve (211.2) are formed the second pressure closed loop control system with described the 3rd pressure sensor (218.1), described the 4th pressure sensor (218.2), described second pressure-reducing valve (216);
Described second solenoid directional control valve (212) control described first hydraulic control one-way valve (113.1), described the 3rd hydraulic control one-way valve (113.3), described the 5th hydraulic control one-way valve (213.1), described the 7th hydraulic control one-way valve (213.3);
Described the 3rd pressure sensor (218.1), described the 4th pressure sensor (218.2) detect the pressure of described second servo-cylinder (217) rodless cavity, rod chamber respectively.
3. system according to claim 1, it is characterized in that described upper joint-shaft is held hydraulic cylinder control system tightly and comprised: the first 3-position 4-way solenoid directional control valve (312), first stacking type hydraulic control check valve (313), the first superposing type Double throttle check valve (314), first pressure switch (315), second pressure switch (316), first oil cylinder (317) and second oil cylinder (318);
The described first 3-position 4-way solenoid directional control valve (312) carries out interlocked control with described first pressure switch (315), described second pressure switch (316);
Described first pressure switch (315) is connected with described second oil cylinder (318) with described first oil cylinder (317) respectively, described second pressure switch (316) is connected with described second oil cylinder (318) with described first oil cylinder (317) respectively, and described first pressure switch (315), described second pressure switch (316) are respectively applied for and detect described first oil cylinder (317) and the rod chamber of described second oil cylinder (318), the pressure of rodless cavity.
4. system according to claim 1, it is characterized in that described bottom spindle is held hydraulic cylinder control system tightly and comprised: the second 3-position 4-way solenoid directional control valve (322), second stacking type hydraulic control check valve (323), the second superposing type Double throttle check valve (324), the 3rd pressure switch (325), the 4th pressure switch (326), the 3rd oil cylinder (327) and the 4th oil cylinder (328);
The described second 3-position 4-way solenoid directional control valve (322) carries out interlocked control with described the 3rd pressure switch (325), described the 4th pressure switch (326);
Described the 3rd pressure switch (325) is connected with described the 4th oil cylinder with described the 3rd oil cylinder (327) respectively, described the 4th pressure switch (326) is connected with described the 4th oil cylinder with described the 3rd oil cylinder (327) respectively, and described the 3rd pressure switch (325), described the 4th pressure switch (326) are respectively applied for and detect described the 3rd oil cylinder (327) and the rod chamber of described the 4th oil cylinder (328), the pressure of rodless cavity.
5. system according to claim 1, it is characterized in that described topping roll axial locking hydraulic cylinder control system comprises: the 3rd 3-position 4-way solenoid directional control valve (332), the 3rd stacking type hydraulic control check valve (333), the 3rd superposing type Double throttle check valve (334), the 5th pressure switch (335), the 6th pressure switch (336), the 5th oil cylinder (337) and the 6th oil cylinder (338);
Described the 3rd 3-position 4-way solenoid directional control valve (332) carries out interlocked control with described the 5th pressure switch (335), described the 6th pressure switch (336);
Described the 5th pressure switch (335) respectively with state the 5th oil cylinder (337) and be connected with described the 6th oil cylinder (338), described the 6th pressure switch (336) respectively with state the 5th oil cylinder (337) and be connected with described the 6th oil cylinder (338), described the 5th pressure switch (335), described the 6th pressure switch (336) are respectively applied for and detect described the 5th oil cylinder (337) and the rod chamber of described the 6th oil cylinder (338), the pressure of rodless cavity.
6. system according to claim 1, it is characterized in that described bottom roll axial locking hydraulic cylinder control system comprises: the 4th 3-position 4-way solenoid directional control valve (342), the 4th stacking type hydraulic control check valve (343), the 4th superposing type Double throttle check valve (344), the 7th pressure switch (345), the 8th pressure switch (346), the 7th oil cylinder (347) and the 8th oil cylinder (348);
Described the 4th 3-position 4-way solenoid directional control valve (342) carries out interlocked control with described the 7th pressure switch (345), described the 8th pressure switch (346);
Described the 7th pressure switch (345) is connected with described the 8th oil cylinder (348) with described the 7th oil cylinder (347) respectively, described the 8th pressure switch (346) is connected with described the 8th oil cylinder (348) with described the 7th oil cylinder (347) respectively, and described the 7th pressure switch (345), described the 8th pressure switch (346) are respectively applied for and detect described the 7th oil cylinder (347) and the rod chamber of described the 8th oil cylinder (348), the pressure of rodless cavity.
7. system according to claim 1, it is characterized in that described first side planisher locking hydraulic cylinder control system comprises: the 5th 3-position 4-way solenoid directional control valve (352), the 5th stacking type hydraulic control check valve (353), the 5th superposing type Double throttle check valve (354), the 9th pressure switch (355), the tenth pressure switch (356), the 9th oil cylinder (357) and the tenth oil cylinder (358);
Described the 5th 3-position 4-way solenoid directional control valve (352) carries out interlocked control with described the 9th pressure switch (355), described the tenth pressure switch (356);
Described the 9th pressure switch (355) is connected with described the tenth oil cylinder (358) with described the 9th oil cylinder (357) respectively, described the tenth oil cylinder (358) is connected with described the tenth oil cylinder (358) with described the 9th oil cylinder (357) respectively, and described the 9th pressure switch (355), described the tenth pressure switch (356) are respectively applied for and detect described the 9th oil cylinder (357) and the rod chamber of described the tenth oil cylinder (358), the pressure of rodless cavity.
8. system according to claim 1, it is characterized in that described second side planisher locking hydraulic cylinder control system comprises: the 6th 3-position 4-way solenoid directional control valve (362), the 6th stacking type hydraulic control check valve (363), the 6th superposing type Double throttle check valve (364), the 11 pressure switch (365), the 12 pressure switch (366), the 11 oil cylinder (367) and the 12 oil cylinder (368);
Described the 6th 3-position 4-way solenoid directional control valve (362) carries out interlocked control with described the 11 pressure switch (365), described the 12 pressure switch (366);
Described the 11 pressure switch (365) is connected with described the 12 oil cylinder (368) with described the 11 oil cylinder (367) respectively, described the 12 oil cylinder (368) is connected with described the 12 oil cylinder (368) with described the 11 oil cylinder (367) respectively, and described the 11 pressure switch (365), described the 12 pressure switch (366) detect described the 11 oil cylinder (367) and the rod chamber of described the 12 oil cylinder (368), the pressure of rodless cavity respectively.
9. system according to claim 1, it is characterized in that described roll change hydraulic cylinder control system comprises: electro-hydraulic proportion reversing valve (372), pressure compensator (373), the 7th stacking type hydraulic control check valve (374), hydraulic pressure bridge circuit (375), first overflow valve (376), roll change oil cylinder (377), first travel switch (378.1), second travel switch (378.2), third trip switch (378.3) and fourth line journey switch (378.4);
Described pressure compensator (373) be superimposed upon electro-hydraulic proportion reversing valve (372) below;
Described the 7th stacking type hydraulic control check valve (374) be superimposed upon pressure compensator (373) below;
Described hydraulic pressure bridge circuit (375) is connected with rod chamber, the rodless cavity of roll change oil cylinder (377) respectively;
Described first travel switch (378.1), described second travel switch (378.2), described third trip switch (378.3) and described fourth line journey switch (378.4) carry out interlocked control with electro-hydraulic proportion reversing valve (372) respectively.
10. system according to claim 1, it is characterized in that described track lifting hydraulic control system comprises: the 7th 3-position 4-way solenoid directional control valve (382), the 8th stacking type hydraulic control check valve (383), balanced valve (384), the 13 pressure switch (385), the 14 pressure switch (386), first cowling panel (387.1), second cowling panel (387.2), first flow speed control valve (388.1), second flow speed control valve (388.2), the 13 oil cylinder (389.1) and the 14 oil cylinder (389.2);
Described the 13 pressure switch (385) is connected with described the 14 oil cylinder (389.2) with described the 13 oil cylinder (389.1) respectively, described the 14 pressure switch (386) is connected with described the 14 oil cylinder (389.2) with described the 13 oil cylinder (389.1) respectively, and described the 13 pressure switch (385), described the 14 pressure switch (386) are respectively applied for and detect described the 13 oil cylinder (389.1) and the rod chamber of described the 14 oil cylinder (389.2), the pressure of rodless cavity.
11. system according to claim 1, it is characterized in that described top working roll balanced hydraulic control system comprises: first throttle valve (411), the first two four-way electromagnetic reversing valves (412), the second two four-way electromagnetic reversing valves (413), the 9th hydraulic control one-way valve (414), second overflow valve (415), the 15 pressure switch (416) and first plunger cases (417);
Described the 15 pressure switch (416) is connected with described first plunger case (417), and described the 15 pressure switch (416) is used to detect the equalizing pressure of described first plunger case (417).
12. system according to claim 1, it is characterized in that described upper joint-shaft balanced hydraulic control system comprises: second choke valve (421), the 3 two four-way electromagnetic reversing valve (422), the 4 two four-way electromagnetic reversing valve (423), the tenth hydraulic control one-way valve (424), the 3rd overflow valve (425), the 16 pressure switch (426), second plunger case (427) and the 3rd plunger case (428);
Described the 16 pressure switch (426) is connected with described the 3rd plunger case (428) with described second plunger case (427) respectively, and described the 16 pressure switch (426) is respectively applied for the equalizing pressure that detects described second plunger case (427) and described the 3rd plunger case (428).
13. system according to claim 1, it is characterized in that described bottom spindle balanced hydraulic control system comprises: the 3rd choke valve (431), the 5 two four-way electromagnetic reversing valve (432), the 6 two four-way electromagnetic reversing valve (433), the 11 hydraulic control one-way valve (434), the 4th overflow valve (435), the 17 pressure switch (436), the 4th plunger case (437) and the 5th plunger case (438);
Described the 17 pressure switch (431) is connected with described the 5th plunger case (438) with described the 4th plunger case (437) respectively, and described the 17 pressure switch (431) is respectively applied for the equalizing pressure that detects described the 4th plunger case (437) and described the 5th plunger case (438).
14. system according to claim 1, it is characterized in that, described hydraulic control system also comprises: the first swing fan-shaped section hydraulic control system, and it further comprises: the 4th choke valve (511), the 7 two four-way electromagnetic reversing valve (512), the 8 two four-way electromagnetic reversing valve (513), the 12 hydraulic control one-way valve (514), the 5th overflow valve (515), the 18 pressure switch (516), the 6th plunger case (517) and the 7th plunger case (518);
Described the 18 pressure switch (516) is connected with described the 7th plunger case (518) with described the 6th plunger case (517) respectively, and described the 18 pressure switch (516) is respectively applied for the equalizing pressure that detects described the 6th plunger case (517) and described the 7th plunger case (518).
15. system according to claim 1, it is characterized in that, described hydraulic control system also comprises: the second swing fan-shaped section hydraulic control system, and it further comprises: the 5th choke valve (521), the 9 two four-way electromagnetic reversing valve (522), the 12 four-way electromagnetic reversing valve (523), the 13 hydraulic control one-way valve (524), the 6th overflow valve (525), the 19 pressure switch (526), the 8th plunger case (527) and the 9th plunger case (528);
Described the 19 pressure switch (526) is connected with described the 9th plunger case (528) with described the 8th plunger case (527) respectively, and described the 19 pressure switch (526) is respectively applied for the equalizing pressure that detects described the 8th plunger case (527) and described the 9th plunger case (528).
CN201120014866XU 2011-01-06 2011-01-06 Hydraulic control system Expired - Fee Related CN202006219U (en)

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Cited By (12)

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CN102513602A (en) * 2011-11-17 2012-06-27 缙云县高新机械制造有限公司 Online monitoring device for drawing bench
CN102728623A (en) * 2012-07-19 2012-10-17 中冶赛迪工程技术股份有限公司 Hydraulic control system for roll balance
CN102758389A (en) * 2012-06-28 2012-10-31 湖南海捷精密工业有限公司 Hydraulic balance loop of mobile device
CN103277364A (en) * 2013-05-27 2013-09-04 陈景华 Locking oil cylinder pressure reducing valve
CN107906069A (en) * 2017-12-12 2018-04-13 南京钢铁股份有限公司 Circumference combines high-quality special steel new small billet withdrawal straightening machine hydraulic valve platform and control method
CN109060387A (en) * 2018-10-30 2018-12-21 北京中车重工机械有限公司 A kind of wheel steering system load simulation experimental rig
CN109570426A (en) * 2019-01-22 2019-04-05 青岛海德马克智能装备有限公司 A kind of clamping control system and radial forging operate machine
CN109604341A (en) * 2018-11-07 2019-04-12 太原重工股份有限公司 Punch and its big lid lifting locking control system
CN110394434A (en) * 2019-08-06 2019-11-01 北京首钢国际工程技术有限公司 A kind of big pressure rolling mill screwdown roller hydraulic control valve platform of continuous casting billet
CN110523778A (en) * 2019-09-25 2019-12-03 马鞍山钢铁股份有限公司 A kind of control method of universal profiled rolling mill upper roller compensating cylinder roll change position
CN111687219A (en) * 2020-06-08 2020-09-22 首钢集团有限公司 Hydraulic system and method for controlling tension of cold rolling single-rack simulator
CN113399474A (en) * 2021-05-26 2021-09-17 舞阳钢铁有限责任公司 Method for quickly pre-judging faults of main connecting shaft of rolling mill roller

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102513602A (en) * 2011-11-17 2012-06-27 缙云县高新机械制造有限公司 Online monitoring device for drawing bench
CN102758389A (en) * 2012-06-28 2012-10-31 湖南海捷精密工业有限公司 Hydraulic balance loop of mobile device
CN102728623A (en) * 2012-07-19 2012-10-17 中冶赛迪工程技术股份有限公司 Hydraulic control system for roll balance
CN102728623B (en) * 2012-07-19 2014-11-12 中冶赛迪工程技术股份有限公司 Hydraulic control system for roll balance
CN103277364A (en) * 2013-05-27 2013-09-04 陈景华 Locking oil cylinder pressure reducing valve
CN107906069A (en) * 2017-12-12 2018-04-13 南京钢铁股份有限公司 Circumference combines high-quality special steel new small billet withdrawal straightening machine hydraulic valve platform and control method
CN107906069B (en) * 2017-12-12 2024-01-09 南京钢铁股份有限公司 Hydraulic valve table of square and round combined small square billet withdrawal and straightening machine and control method
CN109060387A (en) * 2018-10-30 2018-12-21 北京中车重工机械有限公司 A kind of wheel steering system load simulation experimental rig
CN109604341A (en) * 2018-11-07 2019-04-12 太原重工股份有限公司 Punch and its big lid lifting locking control system
CN109570426A (en) * 2019-01-22 2019-04-05 青岛海德马克智能装备有限公司 A kind of clamping control system and radial forging operate machine
CN110394434A (en) * 2019-08-06 2019-11-01 北京首钢国际工程技术有限公司 A kind of big pressure rolling mill screwdown roller hydraulic control valve platform of continuous casting billet
CN110394434B (en) * 2019-08-06 2024-03-29 北京首钢国际工程技术有限公司 Continuous casting billet large-reduction rolling mill reduction roll hydraulic control valve table
CN110523778A (en) * 2019-09-25 2019-12-03 马鞍山钢铁股份有限公司 A kind of control method of universal profiled rolling mill upper roller compensating cylinder roll change position
CN110523778B (en) * 2019-09-25 2020-09-04 马鞍山钢铁股份有限公司 Control method for roll changing position of upper roll balance cylinder of universal section mill
CN111687219A (en) * 2020-06-08 2020-09-22 首钢集团有限公司 Hydraulic system and method for controlling tension of cold rolling single-rack simulator
CN113399474A (en) * 2021-05-26 2021-09-17 舞阳钢铁有限责任公司 Method for quickly pre-judging faults of main connecting shaft of rolling mill roller

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